EP1729037B1 - Transmission d'anneau de friction - Google Patents

Transmission d'anneau de friction Download PDF

Info

Publication number
EP1729037B1
EP1729037B1 EP20050104605 EP05104605A EP1729037B1 EP 1729037 B1 EP1729037 B1 EP 1729037B1 EP 20050104605 EP20050104605 EP 20050104605 EP 05104605 A EP05104605 A EP 05104605A EP 1729037 B1 EP1729037 B1 EP 1729037B1
Authority
EP
European Patent Office
Prior art keywords
actuator
friction
friction ring
ring
ring transmission
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
EP20050104605
Other languages
German (de)
English (en)
Other versions
EP1729037A1 (fr
Inventor
Martin Dr. Leibbrandt
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Getrag Ford Transmissions GmbH
Original Assignee
Getrag Ford Transmissions GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Getrag Ford Transmissions GmbH filed Critical Getrag Ford Transmissions GmbH
Priority to EP20050104605 priority Critical patent/EP1729037B1/fr
Priority to DE200550009189 priority patent/DE502005009189D1/de
Priority to JP2006149368A priority patent/JP4657985B2/ja
Priority to CN2006101495223A priority patent/CN1940349B/zh
Publication of EP1729037A1 publication Critical patent/EP1729037A1/fr
Application granted granted Critical
Publication of EP1729037B1 publication Critical patent/EP1729037B1/fr
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/66—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings
    • F16H61/662—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings with endless flexible members
    • F16H61/66231—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings with endless flexible members controlling shifting exclusively as a function of speed
    • F16H61/66236—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings with endless flexible members controlling shifting exclusively as a function of speed using electrical or electronical sensing or control means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H15/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
    • F16H15/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members without members having orbital motion
    • F16H15/04—Gearings providing a continuous range of gear ratios
    • F16H15/42—Gearings providing a continuous range of gear ratios in which two members co-operate by means of rings or by means of parts of endless flexible members pressed between the first mentioned members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/12—Detecting malfunction or potential malfunction, e.g. fail safe; Circumventing or fixing failures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/68—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for stepped gearings
    • F16H61/684—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for stepped gearings without interruption of drive
    • F16H61/686—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for stepped gearings without interruption of drive with orbital gears

Definitions

  • the invention relates to a conical-ring gearbox with two conical friction wheels arranged opposite each other on parallel shafts and with a friction ring, which engages with both conical friction wheels and surrounds one of the conical friction wheels.
  • a bevel gear or conical friction ring gear is a continuously variable transmission in which the gear ratio can be varied steplessly by adjusting the friction ring in the axial direction of the waves.
  • One way to move the friction ring in the axial direction, is to force him over, for example, a spindle drive.
  • This has several disadvantages.
  • a major drawback is that such positive guidance of the ring is characterized by poor dynamics.
  • a second possibility to adjust the friction ring in the axial direction is in the DE 195 42 726 described.
  • the friction ring can likewise be displaced axially. Due to the tilt angle, slip forces occur on the friction ring depending on the direction of rotation of the two conical friction wheels, which accelerate the friction ring in one or the other direction along the axes of the conical friction wheels.
  • This method of adjustment is characterized by high dynamics and good efficiency.
  • the tilt angle of the friction ring must always be regulated.
  • a pivotable frame whose pivoting angle can be regulated by an adjusting device or by an adjusting mechanism.
  • the frame has two mutually spaced and parallel to the axes of rotation of the conical friction wheels extending rails, which guide a carriage which can be moved axially along the rails.
  • This slidable carriage guides the friction ring, during pivoting the frame is tilted over the slide of the friction ring from a plane perpendicular to the axes of the conical friction wheels running plane.
  • the adjustment mechanism fails, different situations may occur depending on the design, which preclude further use of the transmission, at least in emergency mode. If the adjusting mechanism remains in the position which it had during the failure, the friction ring runs into an axial end position, as far as the position has given a tilt angle in the event of failure. As a result of this, the gear ratio which then arises due to the axial end position of the friction ring corresponds to the minimum or maximum transmission ratio of the conical-ring transmission. If such a conical-ring transmission is used in a motor vehicle, this could practically no longer be used if the adjusting mechanism fails. Either the vehicle could only be driven at very low speed or, in other axial end position of the friction ring, no longer be started from a standstill.
  • the friction ring changes into irregular movement patterns as a function of the transmitted torque. If the adjusting mechanism assumes a neutral position after failure, the friction ring moves into a drive-torque-dependent position.
  • the invention is therefore based on the object to provide a conical-ring gearbox that allows a controllable and in a motor vehicle meaningful emergency operation in case of failure of the adjustment mechanism, as far as it is installed there.
  • the conical-ring transmission according to claim 1 is characterized in that an adjustment device comprising an actuator defines an axial neutral position of the friction ring in the case of a neutral position of the actuator, wherein the adjustment device deviates at axial positions of the friction ring which deviate from the neutral position Neutral position of the actuator Tilt angle in advance the friction ring is moved in the direction of the neutral position.
  • the neutral position can be chosen so that in this position of the friction ring, the cone ring gear has an average gear ratio, which could correspond to the gear ratio of a conventional automotive gearbox in 3rd gear.
  • a motor vehicle equipped with the cone ring gear could still start up and also move at a sufficiently high speed, even if the adjusting device is no longer functional, for example due to a failure of the supply voltage or cable breakage.
  • the adjusting device for the friction ring results in a tilt angle equal to zero. This means that act in this neutral position at least approximately no restoring forces on the friction ring. As soon as the friction ring deviates from the neutral position as a result of external influences, tilting angles which bring the friction ring back into the neutral position are established by the adjusting device or by its geometry.
  • the adjusting device defines a predetermined position of the friction ring in the axial direction for each position of the actuator, wherein at positions which deviate from the predetermined position, the adjustment tipping angle by which the friction ring is moved in the direction of the predetermined position ,
  • each position of the actuator can be assigned exactly one position of the friction ring, wherein in each case a stable position of the friction ring is achieved by the adjustment on the specification of the tilt angle.
  • the actuator may comprise a spring-centered linear proportional solenoid. If the power supply of the actuator fails, a spring ensures the neutral position of the actuator. Such a trained actuator can readily apply the forces necessary for tilting the friction ring, as they are very small.
  • the actuator has a foot point whose position changes as a function of the axial position of the friction ring.
  • the change in the position of the point can be proportional, progressive or degressive to change the axial position of the friction ring.
  • the base of the actuator is connected to a crabddling arrangement.
  • the facedtician entry can be designed as a rail which slidably supports the base of the actuator. The rail thus provides all possible positions of the foot point of the actuator.
  • the guide rail is inclined to the parallel axes of rotation of the conical friction wheels and preferably has a straight course.
  • the guide rail is expediently fixed.
  • the inclination of the guide rail determines the course of the tilt angle as a function of the axial position of the friction ring for a constant position of the actuator.
  • the greater the inclination of the guide rail the more the tilting angle increases, as viewed from the position of the friction ring, in which the tilt angle, due to the adjusting device, has a value equal to zero.
  • the inclination of the guide rail is adjustable.
  • the angle of inclination relative to the axes of the conical friction wheels can be varied.
  • the inventive automatic adjustment of a position in dependence on a specific position of the actuator can also be achieved if the conical friction wheels rotate in a direction opposite to their usual direction of rotation. In a cone ring gear in a motor vehicle this is the case when the motor vehicle is to be moved backwards.
  • the adjusting device may comprise a further actuator in addition to the at least one actuator.
  • the actuators can cooperate in the adjusting device such that a movement of the actuator leads to a reciprocal movement of the other actuator. This opens up the possibility of using actuators with traction magnets whose control and handling is much easier than the handling of so-called push / pull magnets.
  • the crabtician entry can also be designed as a pivoting arm.
  • the swivel arm is rotatably mounted about a pivot axis, wherein the position of the foot point of the actuator changes by the rotation of the swivel arm.
  • the pivot axis can be perpendicular to the parallel axes of the conical friction wheels and cut these two axes.
  • the pivot axis of the pivot arm may be movable with the friction ring in the axial direction of the conical friction wheels.
  • the pivot axis of the pivot arm is not fixed, but is only defined based on the axial position of the friction ring.
  • pivot axis of the pivot arm and friction ring are fixed only relative to each other can be preferably realized by a carriage, wherein a ring guide, for example in the form of a frame for the friction ring and the pivot arm are arranged on the carriage.
  • the slide can be moved parallel to the axes of the bevel gears.
  • the frame specifies the tilt angle for the friction ring, so that the frame as well as the pivot arm is rotatably mounted on the carriage.
  • the distance between the tilting axis of the frame and the pivot axis of the pivoting arm is constant.
  • a transmission unit which converts an axial movement of the friction ring in a pivoting movement of the pivot arm.
  • the position of the foot point of the actuator changes depending on the axial position of the friction ring.
  • the gear unit may comprise at least one cable, which is connected to the pivot arm on the one hand and with a stationary point on the other hand.
  • the cable is in this case attached to the pivot arm, that rotates by a translational movement of the pivot axis of the pivot arm in a certain ratio of the pivot arm about the pivot axis.
  • two opposing cables can be provided to completely fix the base of the actuator.
  • thetician Vietnamese Institution may only comprise a support bearing, which is arranged on the carriage.
  • the relative position of this support bearing relative to the frame in turn depends on the axial position of the friction ring.
  • the case to be provided gear unit for adjusting the Abstweillagers must translate a translational movement of the friction ring in another translational movement of the Abstweillagers.
  • the tilt axis about which the friction ring can be tilted can lie in the plane of the parallel axes of the bevel gears and preferably in the running plane of the friction ring.
  • FIG. 1 shows a cone ring gear, which is designated in its entirety by 1.
  • the bevel ring gear 1 has a first conical friction wheel 2 and a second conical friction wheel 3.
  • the conical friction wheels 2, 3 are arranged opposite to each other, wherein whose axes of rotation are parallel to each other and have a certain distance from each other.
  • the axes of rotation of the conical friction wheels 2, 3 shown by a dashed line 4, wherein in the illustration of FIG. 1 the axis of rotation of Kegelreibrads 3 is behind the axis of rotation of Kegelreibrads 2.
  • a friction ring 5 In order to transmit a torque from the first conical friction wheel 2 to the second conical friction wheel 3, a friction ring 5 is provided, which engages with both conical friction wheels 2, 3 and engages around the first conical friction wheel 2.
  • the friction ring 5 can be tilted about a tilt axis 6, located in the FIG. 1 extends into the drawing plane. As can be seen, the tilting axis 6 intersects the dashed line 4 and thus the two axes of rotation of the conical friction wheels 2, 3.
  • an adjusting device designated 7 In order to tilt the friction ring 5 about the tilting axis 6, an adjusting device designated 7 is provided.
  • the adjusting device 7 comprises a ring guide 8, an actuator 9 and a guide rail 10.
  • the guide rail 10 is inclined to the dashed line 4 and thus to the parallel axes of rotation of the conical friction wheels 2, 3 by an angle.
  • a foot point 11 of the actuator 9 can be moved along the rail 10, wherein the position of the foot point 11 in the Y direction with respect to the axes of the conical friction wheels 2, 3 changes.
  • the friction ring 5 has a tilt angle equal to zero. At this tilt angle equal to zero, the friction ring 5 runs in a plane perpendicular to the two axes of rotation of the conical friction wheels 2, 3, wherein a movement of the friction ring 5 in the direction of the parallel axes of rotation of the conical friction wheels 2, 3, ie in the X direction does not take place.
  • the actuator 9 is connected via an articulation lever 13 to the ring guide 8.
  • the vertical, solid line 14 on the guide rail 10 indicates the position of the foot 11, when the actuator is in a neutral position.
  • This neutral position of the actuator 9 on the line 14 is associated with a corresponding neutral position of the friction ring 5, which corresponds to the in FIG. 1 position shown of the friction ring 5 has a distance.
  • This distance corresponds to the one in FIG. 1
  • the actuator 9 compensates for the offset of the foot point 11 to the neutral position active, so that the friction ring 5 is not tilted.
  • FIG. 1 an arbitrary operating point of the conical-ring gear 1, wherein due to the axial position of the friction ring 5, a certain gear ratio due to the effective radii of the conical friction wheels 2, 3 sets.
  • FIG. 2 shows two cases in which the actuator from an arbitrary operating point of the conical-ring gear 1, for example due to a failure of the control for the actuator 9, assumes its neutral position.
  • the in FIG. 2 , left side, operating point shown here corresponds approximately to the in FIG. 1 illustrated operating point.
  • the friction ring 5 is located to the right of the constructively determined neutral position (see point 11 and line 14). Due to the shifted position of the base 11 of the actuator 9, the friction ring 5 is tilted from its usual running plane by the angle 1 , so that a force acting on the friction ring 5, the ring 5 in the direction of the arrow 15, ie to the left, moves. By the movement of the friction ring 5 in the direction of the arrow 15, the actuator 9 is simultaneously moved in the same direction, the base 11 slides along the guide rail 10 and approaches the intersection of the line 14 and the guide rail 10. Due to the associated base displacement in the Y direction, the angle 1 becomes smaller and smaller until, when the foot point 11 lies on the line 14, it finally assumes the value zero. Since now no more actuating forces act on the friction ring due to the tilt angle equal to zero, it remains in this axial position.
  • the friction ring 5 is in the right half of the FIG. 2 now left of the neutral position of the friction ring 5, in which the base point 11 is located on the line 14.
  • adjusting 7 is now when the actuator 9 assumes its neutral position (this means a certain distance between the foot 11 and the friction ring side end 12), a tilt angle 2 is generated, the angle 1 from the left half of the FIG. 2 is opposite and leads to an axial movement of the friction ring 9 in the direction of the arrow 16, ie to the right.
  • the movement of the friction ring 5 in the direction of the arrow 16 ends again in the neutral position, since there again sets a tilt angle equal to zero.
  • Another method of the friction ring 5 in the direction of the arrow 16 is prevented by the adjusting device 7, which imposes a tilt angle in this case the friction ring 5, which would counteract this movement.
  • FIG. 3 shows a further embodiment of the invention.
  • Components that belong to the components of FIGS. 1 and 2 are identical or are comparable, are marked accordingly with the same reference numerals. The following is only on the main differences to the execution of the FIGS. 1 and 2 received.
  • Trained as a frame ring guide 8 is arranged on a carriage 17 which can be moved along two slide rails 18, 19.
  • the slide rails 18, 19 extend parallel to the axes of rotation of the conical friction wheels 2, 3 (see line 4).
  • a pivot arm 20 which can rotate about a pivot axis 21.
  • the pivot axis 21 is fixedly connected to the carriage 17, so that the distance in the X direction from the frame 8 and the pivot axis 21 is constant.
  • Two actuators 22, 23 are each supported with their base point 11 on the pivot arm 20, wherein the foot points 11 of the two actuators are located at one end of the pivot arm 20.
  • each axial position of the carriage 17 and thus the guided through the frame 8 friction ring 5 is assigned exactly one pivot angle of the pivot arm 20.
  • This in turn means for the actuators 22, 23, that the relative position of the base points 11 changes with the axial position of the friction ring 5.
  • the pivoting angle of the pivoting arm 20 has a value different from zero. If the friction ring is now to be held in this position via the adjusting device 7 in order to realize a specific transmission ratio, the actuators 22, 23 are equal in their distances between the base 11 of the actuator 22 and the frame 8 on the one hand and the one by a corresponding control Base point 11 of the actuator 23 and the frame 8 on the other hand. Now fall the actuators 22, 23 or even one of them, he or she goes to the neutral position with the result that with the help of a spring 25 of the frame 8 and thus also the friction ring 5 is tilted in a plane parallel to the inclined pivot arm 20 is.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Friction Gearing (AREA)
  • Control Of Transmission Device (AREA)

Claims (15)

  1. Transmission à anneau conique (1) comprenant deux roues de friction coniques (2, 3) opposées l'une à l'autre et disposées sur des arbres parallèles, et un anneau de friction (5) qui est en prise avec les deux roues de friction coniques (2, 3) et vient en prise autour de l'une des roues de friction coniques (2, 3), l'anneau de friction (5) pouvant être déplacé axialement par rapport à un plan de roulement s'étendant perpendiculairement aux axes de rotation des roues de friction coniques (2, 3) en prédéfinissant un angle de basculement β, caractérisée en ce qu'un dispositif de réglage (7) comprenant au moins un actionneur (9 ; 22, 23), dans une position neutre de l'actionneur (9 ; 22, 23), fixe une position axiale neutre de l'anneau de friction (5), et dans des positions axiales de l'anneau de friction (5) qui s'écartent de la position neutre, le dispositif de réglage (7), dans la position neutre de l'actionneur (9 ; 22, 23) prédéfinit un angle de basculement β duquel l'anneau de friction (5) est déplacé dans la direction de la position neutre.
  2. Transmission à anneau conique (1) selon la revendication 1, caractérisée en ce que pour chaque position de l'actionneur (9 ; 22, 23), le dispositif de réglage (7) fixe à chaque fois une position prédéterminée de l'anneau de friction (5), et dans les positions qui s'écartent de la position prédéterminée, le dispositif de réglage (7) prédéfinit un angle de basculement duquel l'anneau de friction (5) est déplacé dans la direction de la position prédéterminée.
  3. Transmission à anneau conique (1) selon l'une quelconque des revendications 1 ou 2, caractérisée en ce que l'actionneur (9 ; 22, 23) comprend un aimant proportionnel linéaire centré par ressort.
  4. Transmission à anneau conique (1) selon l'une quelconque des revendications 1 à 3, caractérisée en ce que l'actionneur présente un point de base, dont la position varie en fonction de la position axiale de l'anneau de friction (5).
  5. Transmission à anneau conique (1) selon la revendication 4, caractérisée en ce que le point de base (11) de l'actionneur (9 ; 22, 23) est connecté à un guidage du point de base (10, 20).
  6. Transmission à anneau conique (1) selon la revendication 5, caractérisée en ce que le guidage du point de base est réalisé sous forme de rail de guidage (10) qui supporte de manière déplaçable le point de base (11) de l'actionneur (9).
  7. Transmission à anneau conique (1) selon la revendication 6, caractérisée en ce que le rail de guidage présente une inclinaison vers les axes parallèles des roues de friction coniques (2, 3) et est de préférence droit.
  8. Transmission à anneau conique (1) selon la revendication 6 ou 7, caractérisée en ce que l'inclinaison du rail de guidage (10) est ajustable.
  9. Transmission à anneau conique (1) selon l'une quelconque des revendications 1 à 8, caractérisée en ce que l'on prévoit un actionneur supplémentaire qui coopère avec l'au moins un actionneur.
  10. Transmission à anneau conique (1) selon la revendication 5 ou 9, caractérisée en ce que le guidage du point de base est réalisé sous forme de bras pivotant (20).
  11. Transmission à anneau conique (1) selon la revendication 10, caractérisée en ce qu'un axe de pivotement (21) du bras pivotant (20) est déplaçable avec l'anneau de friction (5) dans la direction des axes des roues de friction coniques (2, 3).
  12. Transmission à anneau conique (1) selon la revendication 11, caractérisée en ce qu'un guide annulaire (8) et le bras pivotant (20) sont disposés sur un chariot (17), qui peut être déplacé parallèlement aux axes des roues de friction coniques (2, 3).
  13. Transmission à anneau conique (1) selon l'une quelconque des revendications 10 à 12, caractérisée en ce que l'on prévoit une unité de transmission (24) qui convertit un mouvement axial de l'anneau de friction (5) en un mouvement de pivotement du bras pivotant (20).
  14. Transmission à anneau conique (1) selon la revendication 13, caractérisée en ce que l'unité de transmission est réalisée sous forme de câble Bowden (24), qui est connecté au bras pivotant (20) et à un point fixe.
  15. Transmission à anneau conique selon l'une quelconque des revendications 1 à 14, caractérisée en ce qu'un axe de basculement (6) autour duquel l'anneau de friction (5) peut basculer, se situe dans le plan des axes de rotation parallèles des roues de friction coniques, de préférence dans le plan de roulement de l'anneau de friction (5).
EP20050104605 2005-05-30 2005-05-30 Transmission d'anneau de friction Expired - Fee Related EP1729037B1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP20050104605 EP1729037B1 (fr) 2005-05-30 2005-05-30 Transmission d'anneau de friction
DE200550009189 DE502005009189D1 (de) 2005-05-30 2005-05-30 Kegelringgetriebe
JP2006149368A JP4657985B2 (ja) 2005-05-30 2006-05-30 円錐リング変速機
CN2006101495223A CN1940349B (zh) 2005-05-30 2006-05-30 锥环变速器

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP20050104605 EP1729037B1 (fr) 2005-05-30 2005-05-30 Transmission d'anneau de friction

Publications (2)

Publication Number Publication Date
EP1729037A1 EP1729037A1 (fr) 2006-12-06
EP1729037B1 true EP1729037B1 (fr) 2010-03-10

Family

ID=34979280

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20050104605 Expired - Fee Related EP1729037B1 (fr) 2005-05-30 2005-05-30 Transmission d'anneau de friction

Country Status (4)

Country Link
EP (1) EP1729037B1 (fr)
JP (1) JP4657985B2 (fr)
CN (1) CN1940349B (fr)
DE (1) DE502005009189D1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102628511A (zh) * 2012-04-17 2012-08-08 浙江午马减速机有限公司 蜗杆自动调速机构

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ATE511037T1 (de) * 2007-11-27 2011-06-15 Rohs Ulrich Kegelreibringgetriebe
JP2010151186A (ja) * 2008-12-24 2010-07-08 Aisin Aw Co Ltd 無段変速機
JP2011202791A (ja) * 2010-03-26 2011-10-13 Aisin Aw Co Ltd 動力伝達装置およびその制御方法
CN102959278B (zh) * 2010-06-24 2015-11-25 乌尔里克·罗斯 锥形摩擦环传动装置
KR101251743B1 (ko) * 2011-01-25 2013-04-05 현대 파워텍 주식회사 콘 링 타입 무단변속기
US9212743B2 (en) * 2012-05-29 2015-12-15 Gm Global Technology Operations, Llc Containment control for a continuously variable transmission
DE102012021171A1 (de) * 2012-10-29 2014-04-30 Ulrich Rohs Kegelreibringgetriebe
CN105673834A (zh) * 2016-03-16 2016-06-15 浙江德孚力汽车变速箱有限公司 锥环式无级变速器传动环控制机构
CN109384022B (zh) * 2018-11-30 2024-01-02 西安法士特汽车传动有限公司 一种卧式安装变速器选挡转换机构

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH03288049A (ja) * 1990-03-30 1991-12-18 Shimpo Ind Co Ltd 摩擦無段変速機
DE19542726B4 (de) 1995-11-16 2006-02-16 Rohs, Ulrich, Dr.-Ing. Kegelreibringgetriebe
NL1014505C2 (nl) * 1999-09-15 2001-03-16 Hamapro Holding B V Continu variabele transmissie.
ES2402127T3 (es) * 2002-09-30 2013-04-29 Rohs, Ulrich Transmisión con anillo cónico de fricción
CN1584368A (zh) * 2003-08-20 2005-02-23 乌尔里克.罗斯 无级变速传动装置

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102628511A (zh) * 2012-04-17 2012-08-08 浙江午马减速机有限公司 蜗杆自动调速机构

Also Published As

Publication number Publication date
DE502005009189D1 (de) 2010-04-22
JP2006336861A (ja) 2006-12-14
JP4657985B2 (ja) 2011-03-23
CN1940349B (zh) 2010-06-02
EP1729037A1 (fr) 2006-12-06
CN1940349A (zh) 2007-04-04

Similar Documents

Publication Publication Date Title
EP1729037B1 (fr) Transmission d'anneau de friction
DE2327260C3 (de) Maschine zur Bearbeitung frischbetonierter Oberflächen
DE1917845C3 (fr)
DE202005002585U1 (de) Elektromotorischer Linearantrieb
DE102013014138B3 (de) Lenkanschlag
DE2004249C3 (de) Getriebeschalthebel-Baugruppe für ein mehrgängiges Fahrzeuggetriebe
DE102019217961A1 (de) Lenksäulenanordnung
EP1984656B1 (fr) Dispositif de changement de vitesse pour une boite de vitesses de vehicule automobile
DE650714C (de) Selbsttaetige Schaltvorrichtung fuer Wechselgetriebe, insbesondere von Kraftfahrzeugen
DE102009001393A1 (de) Steuerstangenanordnung zum Verstellen von Rotorblättern eines Hubschraubers
DE60222101T2 (de) Vorrichtung zum antreiben und damit hergestelltes spannwerkeug
EP0217367B1 (fr) Dispositif de propulsion à deux transmissions hydrostatiques
EP0089385A1 (fr) Poste de conduite pour rouleau tandem
DE2823460A1 (de) Pedalanordnung zur steuerung von motor und getriebe bei kraftfahrzeugen
EP3552874B1 (fr) Siège de véhicule pourvu de console de changement de vitesses réglable
EP1870617B1 (fr) Dispositif d'actionnement pour une transmission d'un véhicule
DE69007402T2 (de) Gestänge zur Kraftübertragung für Kraftfahrzeuge.
DE4216430C2 (de) Reibrollengetriebe mit stufenloser Drehmomentübertragung
WO2011160621A2 (fr) Transmission à cônes et anneau de friction
DE3149889C2 (de) Vorrichtung für die Betätigung von Schaltgetrieben zu Versuchszwecken
DE112015002617B4 (de) Betätigungseinrichtung mit lastabhängiger Übersetzung
DE8911435U1 (de) Fräsmaschine mit Tiefenverstellung und Abstützrollen
DE102018115924A1 (de) Stuhl
DE102018108795B4 (de) Fahrzeugsitz mit verstellbarer Schaltkonsole
DE202017102687U1 (de) Befestigungsvorrichtung für eine Fahrzeugeinrichtung

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU MC NL PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA HR LV MK YU

17P Request for examination filed

Effective date: 20070606

AKX Designation fees paid

Designated state(s): DE FR GB

17Q First examination report despatched

Effective date: 20090210

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REF Corresponds to:

Ref document number: 502005009189

Country of ref document: DE

Date of ref document: 20100422

Kind code of ref document: P

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20101213

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 12

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 13

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 14

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20190417

Year of fee payment: 15

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20190430

Year of fee payment: 15

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20200417

Year of fee payment: 16

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20200530

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200530

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200531

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502005009189

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20211201